CN107120407A - Torque vector control device - Google Patents
Torque vector control device Download PDFInfo
- Publication number
- CN107120407A CN107120407A CN201710102700.5A CN201710102700A CN107120407A CN 107120407 A CN107120407 A CN 107120407A CN 201710102700 A CN201710102700 A CN 201710102700A CN 107120407 A CN107120407 A CN 107120407A
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- Prior art keywords
- key element
- gear
- reaction force
- torsion
- output
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H48/11—Differential gearings with gears having orbital motion with orbital spur gears having intermeshing planet gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/20—Arrangements for suppressing or influencing the differential action, e.g. locking devices
- F16H48/24—Arrangements for suppressing or influencing the differential action, e.g. locking devices using positive clutches or brakes
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H2048/104—Differential gearings with gears having orbital motion with orbital spur gears characterised by two ring gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
- F16H2048/106—Differential gearings with gears having orbital motion with orbital spur gears characterised by two sun gears
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
- F16H2048/364—Differential gearings characterised by intentionally generating speed difference between outputs using electric or hydraulic motors
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/36—Differential gearings characterised by intentionally generating speed difference between outputs
- F16H2048/368—Differential gearings characterised by intentionally generating speed difference between outputs using additional orbital gears in combination with clutches or brakes
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16H—GEARING
- F16H48/00—Differential gearings
- F16H48/06—Differential gearings with gears having orbital motion
- F16H48/10—Differential gearings with gears having orbital motion with orbital spur gears
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Retarders (AREA)
Abstract
The present invention provides torque vector control device, will can minimize arrestment mechanism of the Braking in driving wheel.Possess：Drive motor (2)；Differential attachment (4), the second planetary gears (11) of driving wheel (3b) transmission with the first planetary gears (10) for transmitting moment of torsion from drive motor (2) Xiang Yifang driving wheel (3a) and by moment of torsion from drive motor (2) to the opposing party；Differential use motor, the reaction force key element (17) of either one the transmission moment of torsion into above-mentioned differential attachment (4)；Reversing device, is configured to make the mutual torque reversal of reaction force key element and transmits moment of torsion；Rotary shaft (9), the input key element (12,16) of each planetary gears (10,11) is connected to each other；Rotary part (8), moment of torsion is transmitted from the output shaft (6) of drive motor (2) to differential attachment；And arrestment mechanism (B), make Braking in rotary part (8).
Description
Technical field
The present invention relates to can be set in the distribution of the moment of torsion during right wheel transmission to the left of the output torque of drive motor
The torque vector control device of rate.
Background technology
Following torque vector control device is recorded in patent document 1, the torque vector control device is configured to include：
Differential attachment, the driving wheel of the output torque of drive motor to the left and right is transmitted；And differential use motor, to from differential attachment
The apportionment ratio of the moment of torsion of right wheel transmission to the left is controlled.The differential attachment is configured to include the planet tooth of two single pinion types
Mechanism is taken turns, moment of torsion is transmitted from drive motor to each central gear, each gear ring is in the way of to invert each other via anti-
Rotation mechanism links, and differential use motor and the gear ring of a side link.Moreover, driving wheel is via drive shaft and each planetary gear machine
The planet carrier of structure links.
Patent document 1：International Publication No. 2015/008661
The driving torque of the driving wheel of the left and right of the vehicle for the torque vector control device being equipped with described in patent document 1
Change of apportionment ratio that can be carried out by torque vector control device etc. is controlled as different moments of torsion respectively.The opposing party
Face, the brake force of each driving wheel is produced by the brake apparatus set in each driving wheel.It is arranged at the existing braking of each driving wheel
Device possesses the actuator such as the rotary parts such as disk, drum and friction member, the hydraulic cylinder of the rotary part CONTACT WITH FRICTION, so can
Enough brake force needed for producing, but weight also can be very big, and thus, load becomes big under spring, and vibration, the traveling that there is vehicle body are steady
The possibility of qualitative deterioration.
The content of the invention
The present invention is conceived to above-mentioned technical task and completed, and its object is to provide one kind can to make braking masterpiece
The torque vector control device that arrestment mechanism for driving wheel is minimized.
To achieve these goals, torque vector control device of the invention possesses：Drive motor；Differential attachment, its
With the first planetary gears and the second planetary gears, above-mentioned first planetary gears is configured to include the first input
Key element, the first output key element and the first reaction force key element, moment of torsion is from above-mentioned drive motor to the above-mentioned first input key element
Input, above-mentioned first output key element and the driving wheel of a side link, and above-mentioned first reaction force key element is defeated by reaction torque
Go out the moment of torsion to cause above-mentioned first input key element from the above-mentioned first output key element output, above-mentioned second planetary gears is constituted
It is to include the second input key element, the second output key element and the second reaction force key element, moment of torsion is upward from above-mentioned drive motor
State the input of the second input key element, the driving wheel link of above-mentioned second output key element and the opposing party, above-mentioned second reaction force key element
Reaction torque is exported the moment of torsion of above-mentioned second input key element is exported from the above-mentioned second output key element；It is differential to use horse
Reach, it transmits moment of torsion to either one of above-mentioned first reaction force key element and above-mentioned second reaction force key element；Reversing device,
Its torque reversal for making to act on above-mentioned first reaction force key element and to above-mentioned second reaction force key element transmit；And rotation
Axle, it links the above-mentioned first input key element and above-mentioned second input key element；And rotary part, it is from above-mentioned drive motor
Output shaft transmit moment of torsion to above-mentioned rotary shaft, above-mentioned torque vector control device is characterised by, above-mentioned torque vector control
Device possesses arrestment mechanism, and the arrestment mechanism with above-mentioned rotary part CONTACT WITH FRICTION by optionally producing brake force.
In the present invention, it can also be configured to：In above-mentioned first reaction force key element compared with the above-mentioned first input key element
During with lower speed rotation, above-mentioned first planetary gears is instead made as decelerator function, also, above-mentioned second
When firmly key element is rotated compared with the above-mentioned second input key element with lower speed, above-mentioned second planetary gears is used as deceleration
Device function.
In the present invention, above-mentioned arrestment mechanism can also be configured to：By making above-mentioned rotary part and the above-mentioned first anti-work
Firmly key element or above-mentioned first output key element CONTACT WITH FRICTION, and make above-mentioned rotary part and above-mentioned second reaction force key element
Or above-mentioned second output key element CONTACT WITH FRICTION, make above-mentioned Braking in above-mentioned rotary part.
In the present invention, above-mentioned drive motor, which can also be configured to export the rotary speed for making above-mentioned output shaft, drops
Low braking torque, above-mentioned rotary part is configured to rotate integrally with the output shaft of above-mentioned drive motor.
In the present invention, it can also be configured to, above-mentioned rotary part configuration is in the rotary body different from above-mentioned rotary shaft
On rotation axis.
In the present invention, it can also be configured to, above-mentioned rotary part is the output gear of above-mentioned drive motor.
In the present invention, it can also be configured to, possessing will with above-mentioned first reaction force key element or above-mentioned first output
The first spragging gear and export key element is engaged second with above-mentioned second reaction force key element or above-mentioned second that element is engaged
Spragging gear, above-mentioned arrestment mechanism is configured to：By making above-mentioned rotary part and above-mentioned first spragging gear CONTACT WITH FRICTION, and
Make above-mentioned rotary part and above-mentioned second spragging gear CONTACT WITH FRICTION, make above-mentioned Braking in above-mentioned rotary part.
In the present invention, it can also be configured to, when above-mentioned arrestment mechanism is configured to by electromagnetic force to above-mentioned CONTACT WITH FRICTION
Frictional force be controlled.
In the present invention, it can also be configured to, above-mentioned arrestment mechanism is to be configured to clamp machine between the face of CONTACT WITH FRICTION
The arrestment mechanism of the wet type of oil.
According to the present invention, it is configured to the output shaft of the drive motor from the inscape as torque vector control device
Via rotary part moment of torsion is transmitted to the rotary shaft for the input key element for being linked to each planetary gears.Moreover, being provided with being somebody's turn to do
Rotary part CONTACT WITH FRICTION and the arrestment mechanism for acting on brake force.That is, it is built-in with arrestment mechanism in torque vector control device.Cause
This, make Braking in rotary part using arrestment mechanism so that can Braking in driving wheel, so need not
Existing arrestment mechanism is set in driving wheel, or the arrestment mechanism can be minimized.As a result, can reduce under spring
Load, reduces the vibration of vehicle body, improves riding stability.In addition, the rotary part is in addition to transmitting the function of driving torque,
Also there is the function as brake rotor, so the arrestment mechanism for being built in torque vector control device can be minimized.
According to the present invention, it is configured to transmitted the reaction force key element of moment of torsion with motor from differential and used horse from driving
Up to input torque input key element compare rotated with lower speed when, each planetary gears is used as decelerator function.
Moreover, in the structure shown here, in the case of the rotary speed identical of each output key element, each reaction force key element turns into the shape stopped
State, in addition, in the case where the rotary speed of each output key element is different, each reaction force key element is rotated against, differential to use motor
Rotate with.In the case where so each reaction force key element is rotated against, the rotary speed of each reaction force key element also can be into
For extremely low speed.Therefore, each planetary gears is as decelerator function, so acting on the brake force increase of rotary part
And act on each output key element.As a result, arrestment mechanism can be minimized.
According to the present invention, it is configured to by making rotary part and each reaction force key element or each output key element input block
CONTACT WITH FRICTION, thus makes Braking in rotary part.Therefore, above-mentioned each reaction force key element or each output key element are also made
For brake disc function.As a result, arrestment mechanism can be minimized.
According to the present invention, it is configured to rotary part and is rotated integrally with drive motor.Therefore, easily it is driven and uses motor
Braking torque and arrestment mechanism the adjustment shared of brake force etc..
According to the present invention, configure and rotate on the rotation axis of the rotary body different from linking each rotary shaft for inputting key element
Part.Therefore, the heat of the friction produced by arrestment mechanism is difficult to each rotating member transmission for constituting differential attachment, its result
It is that can suppress the increase of the power loss caused by each rotating member thermal expansion etc..
According to the present invention, be configured to arrestment mechanism by electromagnetic force to CONTACT WITH FRICTION when frictional force constitute.Therefore,
Electrical control drive motor and differential use motor and arrestment mechanism, easily carry out the coordination control of each motor, arrestment mechanism.
According to the present invention, arrestment mechanism is the arrestment mechanism of wet type.Therefore, it is possible to suppress the generation of frictional heat, Huo Zheneng
It is enough to make heat reduction rapidly, so the increasing of power loss caused by each part thermal expansion because transmitting moment of torsion etc. can be suppressed
Greatly.
Brief description of the drawings
Fig. 1 is the signal for illustrating an example of the structure of the torque vector control device of embodiments of the invention
Figure.
Fig. 2 is for illustrating to make planet carrier as the schematic diagram of an example of the composition of brake disc function.
Fig. 3 is for illustrating to make output gear as the signal of an example of the composition of brake rotor function
Figure.
Fig. 4 is an example for illustrating the composition for the output torque for transmitting differential motor to gear ring via spragging gear
Schematic diagram.
Fig. 5 is the schematic diagram for illustrating an example of the composition for linking each spragging gear using reversing device.
Fig. 6 is the schematic diagram for illustrating the composition of the premise as torque vector control device example.
Symbol description
1：Torque vector control device；2：Drive motor；3a、3b：Driving wheel；4：Differential attachment；5：It is differential to use motor；
6、27、42：Output shaft；7、28：Output gear；8、45：Driven gear；9：Rotary shaft；10、11：Planetary gears；12、16：
Central gear；13、17：Gear ring；14、18：Planetary gear；15、19：Planet carrier；20：Reversing device；21、22：Connection shaft；23、
24、25、26：Little gear gear；33a、33b、33c、39：Coil；37、38：Spragging gear；B：Arrestment mechanism.
Embodiment
Fig. 6 diagrammatically illustrates one of the composition of the premise as the torque vector control device that can apply the present invention
Example.Torque vector control device 1 shown in Fig. 6 is configured to include drive motor 2 as drive force source function, will
From the drive motor export moment of torsion to the left and right driving wheel 3a, 3b transmission differential attachment 4 and to driving to the left and right
The differential use motor 5 that the apportionment ratio of the moment of torsion of wheel 3a, 3b transmission is controlled.Drive motor 2 shown in Fig. 6 is configured to
It is identical with the known motor for being arranged at motor vehicle driven by mixed power, electric car etc. as drive force source, for example, can be by permanent
Magnet type syncmotor is constituted.
Output gear 7 is linked with the output shaft 6 of the drive motor 2.It is engaged with and differential attachment in the output gear 7
4 driven gears 8 linked, the rotary shaft 9 that both sides in the axial direction are protruded is linked with the driven gear 8.
The rotary shaft 9 is configured in the mode parallel with the output shaft 6 of drive motor 2, and list is linked with respectively in its both sides
The planetary gears 10,11 of pinion type.In addition, in the following description, the planetary gears of a side is denoted as into first
Planetary gears 10, the second planetary gears 11 is denoted as by the planetary gears of the opposing party.
First planetary gears 10 is configured to include：It is linked to the first central gear 12 of rotary shaft 9；With first sun
Gear 12 is configured on concentric circles and external diameter first gear ring 13 bigger than the external diameter of driven gear 8；With the first central gear 12 with
And first gear ring 13 engage the first planetary gear 14；And by the first planetary gear 14 remain can rotation, and by
One planetary gear 14 remains the first planet carrier 15 that can be revolved round the sun centered on the pivot of the first central gear 12.At this
First planet carrier 15 is linked with the drive shaft of side (not shown).Above-mentioned first central gear 12 is equivalent to embodiments of the invention
" first input key element ", the first gear ring 13 is equivalent to " the first reaction force key element " of embodiments of the invention, the first planet
" first output key element " of the frame 15 equivalent to embodiments of the invention.Above-mentioned first gear ring 13 is formed with external tooth.In addition, of the invention
" the first planetary gears " of embodiment be not limited to the planetary gears or double small tooth of single pinion type
The planetary gears of wheel-type.
In addition, the second planetary gears 11 is configured to identical with the first planetary gears 10, it is configured to include：Link
In the secondary sun wheel 16 of rotary shaft 9；Configured with secondary sun wheel 16 on concentric circles and external diameter is than driven gear 8
The second big gear ring 17 of external diameter；The second planetary gear 18 engaged with the gear ring 17 of secondary sun wheel 16 and second；And will
Second planetary gear 18 remain can rotation, and the second planetary gear 18 is remained can be with secondary sun wheel 16
The second planet carrier 19 revolved round the sun centered on pivot.The driving of opposite side (not shown) is linked with second planet carrier 19
Axle.Above-mentioned secondary sun wheel 16 is equivalent to " the second input key element " of embodiments of the invention, and the second gear ring 17 is equivalent to this
" the second reaction force key element " of the embodiment of invention, " second output of second planet carrier 19 equivalent to embodiments of the invention
Key element ".External tooth is formed with above-mentioned second gear ring 17.In addition, " the second planetary gears " of embodiments of the invention is not
It is confined to the planetary gears of single pinion type or the planetary gears of double-pinion type.
The above-mentioned gear ring 17 of first gear ring 13 and second links via reversing device 20.The reversing device 20 be configured to include with
The mode parallel with rotary shaft 9 configures and remained by housing 32 the first connection shaft 21 and the second connection shaft rotated freely
22.The the first little gear gear engaged with the external tooth of the first gear ring 13 is formed with the end of a side of first connection shaft 21
23, the second little gear gear 24 is formed with the end of the opposing party.In addition, being formed with the end of a side of the second connection shaft 22
The third pinion gear 25 engaged with the external tooth of the second gear ring 17, is formed with and the second little gear gear in the end of the opposing party
The fourth pinion gear 26 of 24 engagements.Above-mentioned second little gear gear 24 is identical with the number of teeth of fourth pinion gear 26.Cause
This, the first connection shaft 21 and the second connection shaft 22 are configured to rotate with identical rotary speed.The reversion constituted as described above
Mechanism 20 in the way of surrounding the outer circumferential side of the first planetary gears 10 and the second planetary gears 11 along the circumferential direction
It is spaced and is provided with multiple as defined in separating.
Also, it is provided with differential use motor 5 to transmit moment of torsion to each gear ring 13,17.The differential use motor 5 can be by
Permanent-magnet type syncmotor, induction motor etc. are constituted.In the example shown in Fig. 6, the output shaft 27 of differential use motor 5 with
The parallel mode of the output shaft 6 of drive motor 2, rotary shaft 9 is configured, and output gear 28 is linked with its leading section.In addition, with
Reversing shaft (countershaft) 29 is configured with the differential mode parallel with the output shaft 27 of motor 5, in the reversing shaft 29
The end of one side is linked with engages and the diameter counter driven gear 30 bigger than output gear 28 with output gear 28.Also,
The diameter reversion driving gear 31 smaller than counter driven gear 30, reversion master are linked with the end of the opposing party of reversing shaft 29
Moving gear 31 is engaged with the external tooth of the second gear ring 17.That is, the moment of torsion for being configured to export from differential use motor 5 increases backward second tooth
Circle 17 is transmitted.In addition it is also possible to be configured to transmit moment of torsion from differential use motor 5 to the first gear ring 13.
It is configured to above-mentioned each planetary gears 11,12, output gear 7,28 etc. and is incorporated in housing 32, to each planet tooth
Take turns mechanism 11,12, the sliding part of output gear 7,28 etc., heating part supply lubrication with or cooling oil.
The effect of torque vector control device 1 to so constituting is illustrated.In the structure shown in Fig. 6, from driving
The moment of torsion exported with motor 2 is transmitted to each central gear 12,16.Now, it is opposite with acting on the moment of torsion of the first central gear 12
The moment of torsion in direction acts on the first gear ring 13, and the moment of torsion of the moment of torsion opposite direction with acting on secondary sun wheel 16 is acted on
In the second gear ring 17.That is, the moment of torsion inputted from drive motor 2 to each planetary gears 10,11 as equidirectional torsion
Square acts on each gear ring 13,17.Unidirectional moment of torsion so is acted on to each gear ring 13,17, but because each gear ring 13,17 is by anti-
Rotation mechanism 20 links, and is cancelled so acting on each gear ring 13,17 moments of torsion.Therefore, each gear ring 13,17 stops in straight traveling etc.
In the state of only, each gear ring 13,17 is used as reaction force key element function.
Therefore, the gearratio for being delivered to the moment of torsion and the first planetary gears 10 of the first central gear 12 correspondingly increases
Exported afterwards from the first planet carrier 15, be delivered to the gearratio phase of the moment of torsion and the second planetary gears 11 of secondary sun wheel 16
It should be exported after ground increase from the second planet carrier 19.As described above, the first planetary gears 10 and the second planetary gears 11
It is identical structure, so the moment of torsion exported from the first planet carrier 15 and the moment of torsion exported from the second planet carrier 19 are same, and
The rotary speed of first planet carrier 15 is identical with the rotary speed of the second planet carrier 19.Driving wheel 3a, 3b transmission i.e., to the left and right
Moment of torsion it is same, driving wheel 3a, 3b of left and right rotary speed are identical.
On the other hand, if will as reaction force from the differential output torque of use motor 5, the second planetary gears 11
The reaction torque change of second gear ring 17 of plain function, so the change in torque exported from the second planet carrier 19.Example
Such as, if from the differential output torque of use motor 5 in the way of increasing the reaction torque of the second gear ring 17, from the second planet
The moment of torsion increase that frame 19 is exported.On the other hand, so in the way of the reaction torque for making the second gear ring 17 increases from difference
In the case of employing the output torque of motor 5, moment of torsion is acted in the way of reducing reaction torque via reversing device 20
In the first gear ring 13.As a result, the moment of torsion reduction exported from the first planet carrier 15.That is, from the differential output torque of use motor 5,
Thus, it is possible to the apportionment ratio for the moment of torsion for changing right wheel 3a, 3b transmission to the left.
Also, in the case that the rotary speed of the driving wheel 3 of left and right is different in turning driving etc., each gear ring 13,17 phases
To rotation, it is accompanied by this, differential use motor 5 rotates.For example, with the second planet carrier 19 link side driving wheel 3b compared with
In the case that the driving wheel 3a for the side that first planet carrier 15 links rotates at a high speed, the first central gear 12 and secondary sun wheel
16 continue to rotate with same rotary speed, so needing the rotary speed between the first planet carrier 15 and the second planet carrier 19
Difference absorbs as the difference of the rotary speed between the gear ring 17 of the first gear ring 13 second.
First gear ring 13 links with the second gear ring 17 via reversing device 20, thus the first gear ring 13 and the second gear ring 17 it
Between rotary speed difference pass through the second gear ring 17, reversion driving gear 31, counter driven gear 30, output gear 28, output
Axle 27 rotates differential use motor 5.In this condition, if making differential use motor 5 produce moment of torsion, above-mentioned rotation can kept
In the state of length velocity relation, change driving wheel 3a, 3b of left and right moment of torsion distribution in good time.
As described above, each gear ring 13,17 rotates to adjust differential amount, its rotary speed is extremely low speed.Therefore, even if
In the case where each gear ring 13,17 rotates, the first planetary gears 10 and the second planetary gears 11 also serve as slowing down
Device function.The moment of torsion for being delivered to the first central gear 12 increases and exported from the first planet carrier 15, is likewise passed to the
The moment of torsion of two central gears 16 increases and exported from the second planet carrier 19.
For the torque vector control device of the present invention, dress is controlled in the torque vector constituted as shown in Figure 6
Arrestment mechanism B is also equipped with putting 1.Illustrate that torque vector control device 1 possesses arrestment mechanism B configuration example below.In addition, following
Explanation in, with Fig. 6 identicals structure mark identical reference marks and the description thereof will be omitted.It additionally, there are housing 32, differential use
Situation of the part that the grade of motor 5 is similarly formed with the example shown in Fig. 6 not shown in Fig. 1~Fig. 5.
In Fig. 1, it is configured to make driven gear 8 as brake rotor function, and makes each gear ring 13,17 as system
Moving plate function.In the example depicted in figure 1, the two sides of the outer circumferential side in driven gear 8 are formed with ring-type
It is touched portion 8a, 8b.In addition, " rotary part " of the driven gear 8 equivalent to embodiments of the invention.
In addition, being formed with the first circle protruded in the axial direction from the side of the side of driven gear 8 in the first gear ring 13
Cylinder portion 13a, is formed with first cylindrical portion 13a front end and is installed in the first planetary gears 10 and driven gear
First contact site 13b of the ring-type between 8.The side of outer circumferential side in first contact site 13b is configured to and is touched portion 8a
Face is contacted, and friction member (not shown) is provided with sideways at this.In addition, inner circumferential side in the first contact site 13b and in radius side
The position of the side-facing depressions of upward driven gear 8 is provided with first coil 33a.In addition, the first contact site 13b and touched portion 8a
Gap be formed as side and the side of driven gear 8 than first coil 33a gap it is small.
For passing through the first contact site 13b and the first cylindrical portion 13a to the first wire 34a that first coil 33a is powered
And first gear ring 13 inside and set, the first terminal part with the side for being arranged at the side of housing 32 in the first gear ring 13
35a connections.Moreover, the first brush 36a for being arranged at housing 32 is contacted with the first terminal part 35a, be configured to via this
One brush 36a is supplied to electric power from battery (not shown).In addition, the first gear ring 13 is made up of spur gear, helical gear etc., constitute
For that can be moved along the axis direction of rotary shaft 9.
In addition, being formed with the second circle protruded in the axial direction from the side of the side of driven gear 8 in the second gear ring 17
Cylinder portion 17a, is formed with second cylindrical portion 17a front end and is installed in the second planetary gears 11 and driven gear
Second contact site 17b of the ring-type between 8.The side of outer circumferential side in second contact site 17b is configured to and is touched portion 8b
Face is contacted, and friction member (not shown) is provided with sideways at this.In addition, inner circumferential side in the second contact site 17b and in radius side
The position of the side-facing depressions of upward driven gear 8 is provided with the second coil 33b.In addition, the second contact site 17b and touched portion 8b
Gap be formed as side and the side of driven gear 8 than the second coil 33b gap it is small.
For passing through the second contact site 17b and the second cylindrical portion 17a to second coil 33b the second wire 34b being powered
And second gear ring 17 inside and set, the Second terminal part with the side for being arranged at the side of housing 32 in the second gear ring 17
35b connections.Moreover, the second brush 36b for being arranged at housing 32 is contacted with Second terminal part 35b, be configured to via this
Two brush 36b are supplied to electric power from battery (not shown).In addition, the second gear ring 17 is made up of spur gear, helical gear etc., constitute
For that can be moved along the axis direction of rotary shaft 9.
The driving-force control apparatus 1 constituted as shown in Figure 1 is powered to each coil 33a, 33b in braking and produces electricity
Magnetic force, thus makes each contact site 13b, 17b and touched portion 8a, 8b CONTACT WITH FRICTION.It can be powered according to each coil 33a, 33b
The current control frictional force.In addition, so each contact site 13b, 17b and touched portion 8a, 8b contact surface clamp it is organic
Oil.That is, the arrestment mechanism B being made up of each gear ring 13,17 and driven gear 8 is electromagnetic brake, and is the brake of wet type
Structure B.
As described above, each planetary gears 10,11 is as decelerator function, so the first central gear 12 is compared
First planet carrier 15 rotate at high speed, and secondary sun wheel 16 compared to the second planet carrier 19 rotate at high speed.Therefore, if such as
Above-mentioned each contact site 13b, 17b like that is contacted with touched portion 8a, 8b, then to first sun in the way of reducing rotary speed
Gear 12 and the action torque of secondary sun wheel 16.Now, in the way of increasing rotary speed to the first gear ring 13 and
The action torque of second gear ring 17, but the first gear ring 13 as described above links with the second gear ring 17 via reversing device 20, so should
Moment of torsion is cancelled.I.e. in braking, identical when also with driving, each gear ring 13,17 is used as reaction force key element function.
Moreover, each contact site 13b, 17b and touched portion 8a, 8b CONTACT WITH FRICTION as described above, thus each planetary gear
Mechanism 10,11 is by differential limitation, so so that the rotary speed of the first central gear 12 and the first planet carrier 15 and the first tooth
The consistent mode of rotary speed of circle 13, it is same so that the to the first central gear 12 and the action torque of the first planet carrier 15
The rotary speed of two central gears 16 and the second planet carrier 19 mode consistent with the rotary speed of the second gear ring 17, to second
The action torque of 16 and second planet carrier of central gear 19.Each planetary gears 10,11 as described above is played as decelerator
Function, so to each planet carrier 15,19 action torques so that its rotary speed is reduced, and the moment of torsion as make to act on it is each too
The moment of torsion of the moment of torsion increase of positive gear 12,16 works.That is, than the braking torque based on the brake force for acting on driven gear 8
Big braking torque acts on each planet carrier 15,19.In addition, from the differential output torque of use motor 5, and change and act on first
In the case of the apportionment ratio of the braking torque of the planet carrier 19 of planet carrier 15 and second, similarly make arrestment mechanism B braking torque
Increase and transmitted to each planet carrier 15,19.
It is configured to the input side to each planetary gears 10,11 as decelerator function as described above, more
Brake force is acted on to the driven gear 8 that the central gear 12,16 as input key element function links for body, is thus made
Braking torque increase based on the brake force is simultaneously transmitted to each planet carrier 15,19, so can minimize arrestment mechanism B.Separately
Outside, it is not necessary to other arrestment mechanism is set in driving wheel 3a, 3b, or can will be arranged at driving wheel 3a, 3b brake
Structure is minimized, so load reduction under so-called spring can be made, the result is that, it is possible to increase riding stability, taking sense.And
And, thus driven gear 8 is not required to as brake rotor function, and each gear ring 13,17 as brake disc function
Arrestment mechanism B other parts are set, can be by the integral miniaturization of driving-force control apparatus 1.
In addition, being the arrestment mechanism B of wet type as described above, so driven gear 8, each gear ring can be suppressed using machine oil
13rd, the generation of 17 frictional heat, or can cool down rapidly.Therefore, driven gear 8, each gear ring 13,17 are made as brake
It in the case of structure B functions, can also suppress the durability reduction of driven gear 8, each gear ring 13,17, or can suppress
Due to the increase of power loss caused by said gear 13,17 thermal expansions etc..And electrical control arrestment mechanism B and each motor
2nd, 5, thus said apparatus 2,5, B coordination control become easy.Moreover, the outer circumferential side in driven gear 8 forms touched portion
8a, 8b, thus act on the brake force for being touched portion 8a, 8b turns into big moment of torsion simultaneously according to the distance at a distance of rotation axis
Work, so touched portion 8a, 8b contact with contact site 13b, 17b pressure can be reduced.In other words, it can reduce to first
The electric current that coil 33a and the second coil 33b is powered.
In addition, the arrestment mechanism of embodiments of the invention is not limited to what driven gear 8 was frictionally engaged with gear ring 13,17
Constitute, can also be configured to the gear to the input torque of differential attachment 4, with differential attachment 4 with reaction force key element or defeated
Go out the rotary part frictional engagement that key element is rotated integrally.Fig. 2 shows that be configured to driven gear 8 connects with the friction of planet carrier 15,19
One example of the driving-force control apparatus 1 of conjunction.In addition, pair with above-mentioned Fig. 6, Fig. 1 identical structure mark identical reference notation
Number and the description thereof will be omitted.In addition, in the example shown in Fig. 2, the structure across the both sides of driven gear 8 is identical, so only saying
The structure of right part in bright figure.
Above-mentioned cylindrical portion 13a, 17a, contact site 13b, 17b are not formed in each gear ring 13,17 shown in Fig. 2, but and Fig. 6
Only be formed as circular in the same manner.On the other hand, in the first small tooth chimeric with the first planetary gear 14 of the first planet carrier 15
The end by the side of driven gear 8 in wheel shaft 15a, the first board member 15b of ring-type can move and one in the axial direction
The mode of body rotation is engaged by spline etc..First board member 15b external diameter is formed as the external diameter substantially phase with driven gear 8
Together, the side and touched portion 8a for being configured to its outer circumferential side are frictionally engaged.Therefore, installed in the first board member 15b outer circumferential side
There is the friction member of ring-type (not shown).
In addition, the inner peripheral portion in the first board member 15b is provided with tertiary coil 33c.Tertiary coil 33c is configured to and schemed
First coil 33a shown in 1 is identical, and is configured to be supplied to electric power from battery (not shown) etc..Specifically, it is configured to logical
Cross in the plate portion 15c with the first pinion shaft 15a ring-types linked in the first pinion shaft 15a and the first planet carrier 15
Portion sets privates 34c, and electric power is supplied to from housing 32 via privates 34c.In addition, being arranged at the privates
The third terminal part 35c of 34c end is configured to contact with being arranged at the third brush 36c of housing 32.
By so constituting, to tertiary coil 33c be powered, the first board member 15b is contacted with touched portion 8a, thus with
Example shown in Fig. 1 is identical, can act on braking torque to driving wheel 3.As a result, can play and Fig. 1 identical effects.
In addition, the gear of CONTACT WITH FRICTION subject side is not limited to driven gear 8 or output gear 7.Also may be used
So that output gear 7 to be constituted as " rotary part " function of embodiments of the invention.Fig. 3 shows the configuration example.
In the example shown in Fig. 3, the first spragging gear 37 is provided with, it is fitting for rotating against with output shaft 6, and with
One gear ring 13 is engaged, and is again provided with the second spragging gear 38, and it is fitting for rotating against with output shaft 6, and with
Two gear rings 17 are engaged.Said gear 37,38 is provided with coil 39 in inner peripheral portion.In addition, the both sides of the outer circumferential side in output gear 7
Face is provided with jut 7a, 7b of ring-type prominent in the axial direction.
It is configured to the side of above-mentioned first spragging gear 37 to contact with the jut 7a of ring-type, and the second spragging gear 38
Side contacted with the jut 7b of ring-type, the side of above-mentioned each spragging gear 37,38 is provided with friction member (not shown).
In addition, across the second spragging gear 37, the side opposite with output gear 7 is provided with parking lock mechanism 40.
Specifically, be configured to output shaft 6 it is coaxial on be provided with parking lock motor 41, by being controlled to the motor 41
System, makes the second spragging gear 38 be contacted with output gear 7.Leading screw is formed with the output shaft 42 of the parking lock motor 41,
The tooth for being formed at the inner peripheral surface of the pressing component 43 of ring-type is engaged with the output shaft 42.That is, it is configured to by using parking lock
Motor 41 is rotated, and thus pressing component 43 is moved in axis direction.Moreover, being configured to lean on the second brake tooth in pressing component 43
The side for taking turns 38 sides is provided with bearing 44, when pressing component 43 is moved to the side of the second spragging gear 38, will via the bearing 44
Second spragging gear 38 is pressed to the side of output gear 7.
Therefore, the second spragging gear 37 is made to be contacted with output gear 7 by rotating parking lock motor 41, then
Even if not being powered to motor 41, the state that can also maintain the second spragging gear 37 to be contacted with output gear 7.That is, it is able to maintain that and stops
Car lock-out state.
In the case where constituting as shown in Figure 3, it can play and the structure identical effect shown in Fig. 1.In addition,
In structure shown in Fig. 3, more specifically the structure member different from differential attachment 4, be arranged on the rotations different from rotary shaft 9
Output gear 7 on shaft axis has the function of brake rotor concurrently, so in the case where frictional contact surface generates heat, can also suppress
Heat is transmitted to differential attachment 4.Therefore, it is possible to suppress the part thermal expansion for constituting differential attachment 4, so can suppress due to this
The power loss that thermal expansion is produced.Also, it is not that will be configured as the part of brake with drive shaft on coaxial, so can
Shorten with drive shaft it is coaxial on width.
Also, in the structure shown in Fig. 3, there is no gear iso-variable velocity device between drive motor 2 and arrestment mechanism B,
So in braking, carrying out Regeneration control to drive motor 2, and braking torque is acted on driving using arrestment mechanism B
In the case of wheel 3, sharing waiting and adjust with motor 2 and arrestment mechanism B braking torque is easily driven.In addition it is also possible to
It is arranged to engage with the second spragging gear with motor 5 by differential as shown in Figure 4.
Furthermore, it is also possible to which as shown in Figure 5, reversing device 20 is arranged to and the first spragging gear 37 and the second braking
Gear 38 is engaged, and driven gear 45 is integrally formed with third pinion gear 25, makes the output gear of differential use motor 5
28 engage with the driven gear 45.By so constituting, the external diameter of driven gear 8 can be made bigger than the external diameter of each gear ring 13,17,
So the moment of torsion inputted from drive motor 2 to differential attachment 4 can be increased.In addition, can reduce due to setting reversing device
The amount that the downward side in bottom of the differential attachment 4 of vertical caused by 20 is protruded.It is relatively low therefore, it is possible to which drive shaft is formed at
Position, so can make the drive shaft leading section installation ball-and-socket joint (not shown) inclination angle reduction, can press down
Brake force is reduced to the transmission efficiency of driving wheel 3.
Claims (9)
1. a kind of torque vector control device, possesses：
Drive motor；
Differential attachment, it has the first planetary gears and the second planetary gears, the first planetary gears structure
As including the first input key element, the first output key element and the first reaction force key element, moment of torsion from the drive motor to
The first input key element input, the first output key element and the driving wheel of a side link, the first reaction force key element
Reaction torque is exported to cause the moment of torsion of the first input key element to be exported from the described first output key element, described second
Planetary gears is configured to include the second input key element, the second output key element and the second reaction force key element, and moment of torsion is from institute
Drive motor is stated to the described second input key element input, the driving wheel link of the second output key element and the opposing party are described
Second reaction force key element exports reaction torque the moment of torsion of the second input key element is exported from described second
Key element is exported；
Differential use motor, it passes moment of torsion to either one of the first reaction force key element and the second reaction force key element
Pass；
Reversing device, its torque reversal for making to act on the first reaction force key element and to the second reaction force key element
Transmission；And
Rotary shaft, it links the described first input key element and the second input key element；And
Rotary part, from the output of the drive motor, axially the rotary shaft transmits moment of torsion for it,
The torque vector control device is characterised by,
The torque vector control device possesses arrestment mechanism, the arrestment mechanism by optionally with the rotary part friction
Contact and produce brake force.
2. torque vector control device according to claim 1, it is characterised in that
It is configured to：When the first reaction force key element is rotated compared with the described first input key element with lower speed, institute
The first planetary gears is stated as decelerator function, also, it is defeated in the second reaction force key element and described second
When entering key element compared to being rotated with lower speed, second planetary gears is used as decelerator function.
3. torque vector control device according to claim 1 or 2, it is characterised in that
The arrestment mechanism is configured to：By making the rotary part and the first reaction force key element or described first defeated
Go out key element CONTACT WITH FRICTION, and the rotary part is rubbed with the second reaction force key element or the second output key element
Contact is wiped, makes the Braking in the rotary part.
4. torque vector control device according to claim 1 or 2, it is characterised in that
The drive motor is configured to export the braking torque that the rotary speed for making the output shaft is reduced,
The rotary part is configured to rotate integrally with the output shaft of the drive motor.
5. torque vector control device according to claim 4, it is characterised in that
The rotary part configuration is on the rotation axis of the rotary body different from the rotary shaft.
6. torque vector control device according to claim 5, it is characterised in that
The rotary part is the output gear of the drive motor.
7. the torque vector control device according to any one of claim 4 to 6, it is characterised in that
Possess with the first reaction force key element or first first spragging gear that engages of output key element and with institute
The second spragging gear of the second reaction force key element or the second output key element engagement is stated,
The arrestment mechanism is configured to：By making the rotary part and the first spragging gear CONTACT WITH FRICTION, and make institute
Rotary part and the second spragging gear CONTACT WITH FRICTION are stated, makes the Braking in the rotary part.
8. torque vector control device according to any one of claim 1 to 7, it is characterised in that
The frictional force that the arrestment mechanism is configured to by electromagnetic force during to the CONTACT WITH FRICTION is controlled.
9. torque vector control device according to any one of claim 1 to 8, it is characterised in that
The arrestment mechanism is the arrestment mechanism for being configured to clamp the wet type of machine oil between the face of CONTACT WITH FRICTION.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP2016-032822 | 2016-02-24 | ||
| JP2016032822A JP6356715B2 (en) | 2016-02-24 | 2016-02-24 | Torque vectoring device |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107120407A true CN107120407A (en) | 2017-09-01 |
| CN107120407B CN107120407B (en) | 2019-08-16 |
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ID=59522267
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710102700.5A Active CN107120407B (en) | 2016-02-24 | 2017-02-24 | Torque vector control device |
Country Status (4)
| Country | Link |
|---|---|
| US (1) | US10436302B2 (en) |
| JP (1) | JP6356715B2 (en) |
| CN (1) | CN107120407B (en) |
| DE (1) | DE102017102880A1 (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111322372A (en) * | 2018-11-29 | 2020-06-23 | 株式会社捷太格特 | Differential device for vehicle |
| CN113446375A (en) * | 2020-03-24 | 2021-09-28 | 丰田自动车株式会社 | Torque vector control device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2015008325A1 (en) * | 2013-07-16 | 2015-01-22 | 株式会社アルケミカ | Driving gear device |
| JP6325586B2 (en) | 2016-02-18 | 2018-05-16 | トヨタ自動車株式会社 | Motor drive unit |
| JP6475187B2 (en) * | 2016-04-28 | 2019-02-27 | トヨタ自動車株式会社 | Drive device |
| JP6475188B2 (en) * | 2016-04-28 | 2019-02-27 | トヨタ自動車株式会社 | Drive device |
| US10300905B2 (en) * | 2017-05-30 | 2019-05-28 | GM Global Technology Operations LLC | Electric vehicle drive using combined differential and reduction gearing |
| KR102067535B1 (en) * | 2018-03-16 | 2020-01-17 | 세일공업 주식회사 | Driving motor integrated transmission |
| US11085516B2 (en) | 2018-09-17 | 2021-08-10 | Ford Global Technologies, Llc | Methods and system for operating a torque vectoring electric machine |
| JP2020099119A (en) * | 2018-12-17 | 2020-06-25 | トヨタ自動車株式会社 | Vehicle drive system |
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- 2017-02-08 US US15/427,357 patent/US10436302B2/en active Active
- 2017-02-14 DE DE102017102880.3A patent/DE102017102880A1/en not_active Ceased
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| DE102005003509A1 (en) * | 2005-01-26 | 2006-07-27 | Voith Turbo Gmbh & Co. Kg | Differential unit e.g. limited slip differential unit, for drive system of e.g. rail vehicle, has hydro motors connected to outputs of gears that are attached to three shaft gears and unit for controlling power train through hydro motors |
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Also Published As
| Publication number | Publication date |
|---|---|
| DE102017102880A9 (en) | 2017-11-02 |
| JP2017150556A (en) | 2017-08-31 |
| DE102017102880A1 (en) | 2017-08-24 |
| JP6356715B2 (en) | 2018-07-11 |
| CN107120407B (en) | 2019-08-16 |
| US20170241532A1 (en) | 2017-08-24 |
| US10436302B2 (en) | 2019-10-08 |
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